Refrigerant powered actuated ball valve

ABSTRACT

A refrigerant powered actuated ball valve for use in the fluid circuit of a refrigeration or air conditioning system which can be remotely controlled by a low amperage control signal is disclosed. The actuated ball valve harnesses the pressurized refrigerant from the fluid circuit in which it is installed as the primary power medium to actuate the valve. The valve includes actuation means with a manifold having an inlet port which is in constant fluid communication with a high-pressure side of the fluid circuit. Pressurized refrigerant supplied to the manifold is branched to a series of fluid channels running through the manifold. Exhaust port operators are mounted in conjunction with the manifold to connect the actuation means to the low-pressure side of the fluid circuit and to direct the flow of pressurized refrigerant to either an exhaust port or the manifold. A reciprocal member disposed within the manifold engages a pinion such that a linear displacement of the reciprocal member causes a corresponding angular displacement of the pinion member. Cycling of the ball valve between an opened position and a closed position is achieved when the pressurized refrigerant is applied to the reciprocal member thereby causing a stem operator on the ball valve to rotate.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates generally to valves for use in the fluidcircuits of refrigeration and air conditioning systems and, moreparticularly, to actuated ball valves, such as compressor valves andline service valves, employing pressurized refrigerant from the fluidcircuit as the primary power medium to achieve valve actuation.

2. Discussion

In the past, the refrigeration and air conditioning industry hastolerated the occurrence of inefficiencies through energy loss which hasbeen observed in refrigeration and air conditioning systems. However,due to the increasing awareness of energy conservation and the attendantneed to design and develop more energy efficient refrigeration and airconditioning systems, it has become necessary to improve upon the energyefficiency of refrigeration and air conditioning systems and componentsby reducing or eliminating any associated energy loss experienced withthem. Improving the efficiency of refrigeration and air conditioningsystems and components may enable fewer compressors to be used in agiven application or enable a fixed number of compressors to work forshorter periods of time, or at less than peak output, thus saving notonly significant amounts in operating costs in the form of electricalenergy, but also significant equipment acquisition, repair andmaintenance costs as well. This becomes particularly significant in manycommon refrigeration and air conditioning applications, such as therefrigeration or freezer section of a grocery store or supermarket or inthe air conditioning system of a large office building, for example,where a series of several compressors may be utilized in a singlesystem.

Valves, such as compressor valves and line service valves, have beencommonly used in refrigeration and air conditioning systems fluidcircuits to direct the flow of refrigerant through the circuit or retainthe charge of liquid or gaseous refrigerant while isolating a portion ofthe circuit so as to facilitate the repair and/or replacement of systemcomponents or to perform general system maintenance, without allowingany of the refrigerant to escape into the atmosphere. It is well-knownthat refrigerants, especially chloroflurocarbons (CFCs), used inrefrigeration and air conditioning systems have a detrimental effect onthe ozone layer of the Earth's atmosphere when released from therefrigeration system into the environment. To this end, Federallegislation has been exacted that has mandated strict requirementsdirected toward the elimination of the release of CFCs into theatmosphere. Furthermore, the unauthorized venting of CFCs to theatmosphere can result in stiff fines and penalties against violators.

To significantly improve the overall energy efficiency of arefrigeration or air conditioning system and to minimize the unwantedrelease of refrigerant from the fluid circuit to atmosphere, it has beenconsidered important to be able to remotely control the actuation ofsystem components, including compressor valves and line service valves.

For example, the ability to remotely close a line service valve inresponse to the detection of a leak in the fluid circuit of arefrigeration or air conditioning system could prevent the unwantedrelease of significant amounts of CFCs into the atmosphere. Also, theshut-down of a refrigeration or air conditioning system for maintenance,energy conservation during off-peak loads, or a variety of other plannedand unplanned reasons could coincide with the automatic closure of aline service valve to maintain a stored charge of refrigerant underpressure. In addition, remote actuation of compressor or line servicevalves would be convenient where manual operation of the valve isdifficult or not practical.

To this end, modest attempts have been made to design remotelycontrolled or actuated valves for use in the fluid circuits ofrefrigeration and air conditioning systems.

One example of an actuated valve which has seen widespread use in therefrigeration and air conditioning industry for remotely controlling theflow of refrigerant through a fluid circuit is a solenoid-operatedglobe-type valve and is generally illustrated in prior art FIG. 1.

The valve 200 includes a body member 202 having a first and a secondfluid passage 204, 206 running therethrough which, when combined,provide a fluid passage through the entire valve 200. Standard fluidfittings 208 located at the ends of the first and second fluid passages204, 206 enable the valve 200 to be easily installed in a fluid circuit.Disposed between the first and second fluid passages 204, 206 at anupper portion 210 of the body member 202 is a solenoid 212. The solenoid212 is affixed to the body member 202 by any of several suitable means,such as welding, brazing or soldering, as generally indicated at 214, orwith a threaded connection. The solenoid 212 includes a plunger operator216 which is disposed for linear movement within the valve body 202 uponenergization of the solenoid 212. At one end of the plunger operator 216is a globe type plug or closure element 218 that is operable tocompletely shut off the fluid passage 204 when in the closed position. Aspring member 220 is placed about the plunger operator 216 and biasedagainst the closure element 218. The plunger operator 216 is linearlypositionable between a closed position (not shown) and an openedposition (as shown in FIG. 1) when the solenoid 212 is energized fromits de-activated state. In the opened position, the closure element 218is withdrawn from the valve seat 222 by the electromagnetic forcegenerated in the solenoid 212, overcoming the bias of the spring member220. Fluid is then free to flow through the fluid passages 204, 206 ofthe valve as indicated by arrows 224. In the closed position, thesolenoid 212 is de-activated and the biasing force of the spring member220 causes the closure element 218 to advance into the fluid passage 204and into engagement against the valve seat 222. When closed, fluid flowthrough the valve 200 is prohibited.

It is significant to note that, as illustrated in FIG. 1, even when thevalve is in the opened position, the closure element of the solenoidvalve remains at least partially protruding into the fluid flow stream.Because of this inherent design feature, blockage or interference withinthe fluid passage is created and, the fluid flow through the valvebecomes turbulent, resulting in an increased pressure drop across thevalve. The pressure drop, in turn, reduces the efficiency of the valveby allowing a significant amount of energy to be lost from therefrigeration circuit. Consequently, this energy loss presents a designconstraint that must be addressed by refrigeration and air conditioningsystem designers and engineers as they develop refrigeration and airconditioning systems. Often, to compensate for the energy loss, systemdesigners and engineers specify larger, over-sized compressors whichexceed the thermodynamic requirements of the refrigeration systemapplication. The use of such oversized compressors is inefficient and awaste of energy.

Solenoid-actuated valves which have been used in the prior art alsopresent other difficulties. One problem results from the fact that thereis no control over the speed at which the valve is closed because theswitching of the valve between its opened and closed positions occursnearly instantaneously. As such, the potential exists for the creationof a detrimental condition within the fluid circuit known as a "fluidhammer" effect. When a valve is closed too quickly, a "fluid hammer"caused by the force of the moving fluid against the closure element, cancreate a significant, momentary spike in the fluid pressure within thevalve, often times substantially exceeding the pressure capacity for thevalve. In many cases, cracks or breaks which are brought on in the fluidlines by a fluid hammer result in the undesirable loss of refrigerant toatmosphere. In some extreme situations, the fluid hammer effect couldcause the valve, itself, to break apart creating an undesirable result.

Also, solenoid-actuated valves typically require a considerable draw ofelectrical current for their operation. As can be readily appreciated,the closure element of the solenoid-actuated valve must be sufficientlybiased by the spring member in order to overcome the force of thepressurized fluid in the circuit and to engage the valve seat toprohibit the flow of fluid through the valve. In turn, theelectromagnetic force generated by the solenoid must overcome the springbias in order to open the valve. This requires that a sufficient amountof electrical energy be received at the solenoid from a remote powersource. The amount of energy necessary to operate a solenoid-actuatedvalve of this type is on the order of 10-12 amps.

Consequently, any efficiency gains to the fluid circuit that areattributable to remote control of the solenoid-actuated valve are morethan offset by the efficiency reductions due to the inherent energylosses resulting from flow turbulence and substantial pressure dropacross the globe-type valve, the increased operating costs associatedwith the cost of the valve as well as with the energy required foroperation of the valve and, finally, the concerns that could begenerated as a result of the occurrence of the "fluid hammer" effect.

For these reasons, ball valves are generally preferred for applicationsin refrigeration and air conditioning fluid circuits because, amongother advantages, they exhibit high efficiency fluid flowcharacteristics and they allow some degree of control over the speed atwhich the valve is closed. However, the ball valves used inrefrigeration and air conditioning systems today, including compressorvalves and line service valves, are primarily (if not exclusively)manually operated.

Prior attempts have also been made to design a remotely controlled,actuated ball valve for use in refrigeration and air conditioningsystems. However, no mechanism for the efficient, controlled actuationof a ball valve disposed within a fluid circuit has, as yet, beenembraced by the refrigeration and air conditioning industry.

One prior art actuated ball valve comprised an electric, motor-drivenactuation mechanism employing a worm gear. The worm gear, in turn, drovea pinion connected to a stem operator of the ball valve. A limit switchcontrolling the revolutions of the motor (and worm gear) consequentlycontrolled the rotation of the ball valve between the opened positionand the closed position. However, this type of actuated ball valve hasnot received widespread acceptance in the refrigeration and airconditioning industry for several reasons. One reason is that the amountof torque required to cycle the ball valve between the opened and closedpositions necessitates an electric motor having a high amperageelectrical draw (e.g. on the order of 15 amps), thereby significantlyincreasing the power requirements for actuation of the valve. Inaddition, because the components of these prior actuated ball valveswere not optimally designed to operate with one another, additionalcomponents were necessary to interface a controller to the actuationunit, increasing the cost and complexity of the actuated valve. Inshort, such prior art actuated ball valves are cost prohibitive.

It is, therefore, an objective of the present invention to provide anactuated ball valve for use in the fluid circuit of a refrigeration orair conditioning system, such as a compressor valve or line servicevalve, which provides an efficient and cost effective means for remotelycontrolling the actuation of the ball valve.

It is another objective of the present invention to provide such anactuated ball valve that exhibits significantly improved fluid flow overprior art actuated valves.

It is still another objective of the present invention to provide suchan actuated ball valve which reduces or eliminates the potential forcreating the "fluid hammer" effect within the fluid circuit.

It is a further objective of the present invention to provide such anactuated ball valve which harnesses the power of the pressurizedrefrigerant in the fluid circuit as the primary power medium to achievevalve actuation.

It is yet an additional objective of the present invention to providesuch an actuated ball valve which can be directly coupled to a remotecontrol system, such as a microprocessor, which generates controlsignals on the order of milli-amps.

SUMMARY OF THE INVENTION

Accordingly, the present invention is directed to a refrigerant poweredactuated ball valve for use in the fluid circuit of a refrigeration orair conditioning system, such as a compressor valve or line servicevalve, which can be remotely controlled by a low amperage controlsignal. The actuated ball valve harnesses the pressurized refrigerantfrom the fluid circuit in which it is installed as the primary powermedium to achieve valve actuation.

The actuated ball valve generally includes a ball valve and an actuationmeans. The actuation means has a manifold having an inlet port which isin constant fluid communication with a high-pressure side of the fluidcircuit. Pressurized refrigerant supplied to the manifold is branched toa series of fluid channels running through the manifold. Two exhaustport operators are mounted in conjunction with the manifold. Eachexhaust port operator has an outlet or exhaust port that connects theactuation means to the low-pressure side of the fluid circuit. Inaddition, each is capable of directing the flow of pressurizedrefrigerant to either the exhaust port or the series of fluid channelsrunning through the manifold. A reciprocal member, such as a rack gear,is disposed for linear movement within a chamber in the manifold. Apinion member engages the reciprocal member such that a lineardisplacement of the reciprocal member causes a corresponding angulardisplacement of the pinion member. A linear displacement is achievedwhen the pressurized refrigerant is applied to the reciprocal memberthereby causing a stem operator on the ball valve to rotate, cycling theball valve between an opened position and a closed position.

The actuated ball valve of the present invention substantially improvesthe energy efficiency over the prior art actuated valves used inrefrigeration and air conditioning systems. The present actuated ballvalve, thus, contributes to the increase in efficiency of therefrigeration or air conditioning system as a whole, permitting greaterrefrigeration and air conditioning system performance and improvedenergy efficiency ratings. This will, in turn, lower the acquisition,operation and maintenance costs of such systems by virtue of the abilityto reduce energy consumption, as well as the size and/or number ofcompressors and other components required for a given refrigeration orair conditioning application.

BRIEF DESCRIPTION OF THE DRAWINGS

The various advantages of the present invention will become apparent toone skilled in the art upon reading the following description of thepreferred embodiments, in which:

FIG. 1 depicts a transverse cross-sectional view of a prior artsolenoid-actuated globe-type valve for use in the fluid circuit of arefrigeration or air conditioning system, shown in the opened position;

FIG. 2 is a schematic plan view of a fluid circuit of the type for usein a refrigeration or air conditioning system including a schematicrepresentation of a refrigerant powered actuated ball valve constructedaccording to the teachings and principles of the present invention shownboth in a first location (solid lines) and in an alternate location(phantom lines);

FIG. 3 represents a simplified transverse cross-sectional view of anactuated ball valve of the type for use in the fluid circuit of arefrigeration or air conditioning system and constructed according tothe teachings and principles of a first embodiment of the presentinvention;

FIG. 4 is an enlarged fragmentary detail view showing a preferred rackand pinion arrangement of the actuation means of the actuated ball valveof FIG. 3; and

FIG. 5 represents a simplified transverse cross-sectional view of anactuated ball valve of the type for use in the fluid circuit of arefrigeration or air conditioning system and constructed according tothe teachings and principles of a second embodiment of the presentinvention.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

It should be understood from the outset that while the drawings and thefollowing discussion relate to particular embodiments of the presentinvention, these embodiments merely encompass what is presently regardedas the best mode of practicing the invention and other modifications maybe made to the particular embodiments without departing from the spiritand scope of the invention.

Referring now to FIGS. 2-7, a refrigerant driven actuated ball valve 10of the present invention is shown and described. As illustrated in theschematic plan view of FIG. 2, an actuated ball valve 10 is installed ina fluid circuit 12 of a refrigeration or air conditioning system. Inaddition to the actuated ball valve 10 of the present invention, thefluid circuit 12 is also shown to generally include a compressor 14, acondenser 16, an expansion valve 18 and an evaporator 20. Arrows 22indicate the direction of fluid flow through the circuit 12. A controlmeans 24 for controlling the operation of the actuated ball valve 10,which could comprise either a simple switch, such as a pressuretransducer or thermostat, or a computer, such as a microprocessor or aprogrammable logic controller, to name a few, is generally indicated at24.

As is well-known, the operating fluid (i.e. refrigerant) of arefrigeration or air conditioning system flows through the fluid circuit12 under pressure, which varies depending upon where in the fluidcircuit 12 the operating fluid is located. For example, the refrigerantis subjected to a lower pressure at the input side of the compressor 14and a higher pressure at the discharge side of the compressor 14.Consequently, the individual portions of the fluid circuit generallyindicated at 26 and 28 can be referenced with greater particularity withthe terms "low pressure side," or simply "low side," and "high pressureside," or simply "high side," respectively.

The actuated ball valve 10 of the present invention can be disposed oneither the high pressure side 28 or the low pressure side 26 of thefluid circuit 12 as shown in FIG. 2, with the schematic representationof a first embodiment of the actuated ball valve 10 disposed in the lowside 26 of the fluid circuit 12 and a second embodiment of the presentinvention 10' (shown in phantom lines) being depicted in the high side28 of the fluid circuit 12. Regardless of the particular location of theactuated ball valve 10, 10', separate fluid line connections 30, 30',32, 32' are provided between the valve and both the high side 28 and lowside 26 of the fluid circuit 12. The fluid connections 30, 30', 32, 32'can be achieved by any of a variety of standard fluid line connections,including face seal fittings, flange fittings, flare fittings, pipefittings and soldered fittings, to name a few, all of which arewell-known in the industry. However, it is contemplated that thepreferred embodiment of the present invention would incorporate aone-quarter inch (1/4") diameter fluid connection having a flarefitting.

With particular reference now FIGS. 3 and 4, a refrigerant poweredactuated ball valve 10 that is constructed according to a firstembodiment of the of the present invention is shown in greater detail.The actuated ball valve 10 generally includes a ball valve 34 and anactuation means 36 for carrying out the instructions commanded by thecontrol means 24. The ball valve 34 and the actuation means 36 areassembled for operation by means of a connection bracket 38 and threadedfasteners 40. This arrangement enables the ball valve 34 and/oractuation means 36 to be disassembled for ease of replacement, serviceor repair. Alternatively, the connection bracket 38 can be permanentlyassembled to the ball valve 34 and/or actuation means 36 by any othersuitable fastening means, such as welding.

The ball valve 34 employed in the actuated ball valve 10 of the presentinvention can be any one of a number of different types of ball valves,such as a straight through or bi-directional ball valve 34', as shown inFIG. 5, a 90° ball valve or a three-way valve 34 for multiple flow pathfluid circuits, as illustrated in the FIG. 2. Further, the ball valve 34employed in the present invention can comprise a ball valve such as thatdisclosed in U.S. Pat. No. 5,397,100 to Kent A. Miller and assigned tothe assignee of the present invention, the teachings of which are herebyexplicitly incorporated by reference. Of course it is appreciated thatthe particular type of ball valve 34 employed in the present inventiondepends on the requirements of the fluid circuit 12 in which it isinstalled and the scope of present invention is not intended to belimited to any one model of ball valve.

Furthermore, the preferred embodiment of the present inventioncontemplates incorporating a ball valve 34 which can range in size fromone-quarter of an inch (1/4") to upwards of three and one-eighths inches(31/8") or more.

Referring now to the ball valve 34 shown in FIG. 3, the ball valve 34generally incorporates a body section 42 and tail section 44. Fluid lineconnector portions 46, 47 and 48 serve to connect the ball valve 34 tothe fluid circuit 12 of a refrigeration system. The fluid line connectorportions 46, 47 and 48 may be compatible with any of a variety ofstandard fluid line connections, including face seal fittings, flangefittings, flare fittings, pipe fittings and soldered fittings, to name afew, all of which are well-known in the industry. The body section 42and the tail section 44 of the ball valve 34 are alignably connectableto one another, such as by a threaded engagement to form a unitary valvebody after the installation and assembly of the ball valve's 34 internalcomponents has been completed. A sealed connection between the bodysection 42 and the tail section 44 can be achieved by any suitablemethod, such as welding, brazing, soldering or the like. Although thebody of the ball valve 34 has been described as having a multi-componentconstruction including the body section 42 and the tail section 44, itshould be appreciated that the body of the ball valve 34 may also bemanufactured as a single component.

Also shown in FIG. 3, a generally spherically-shaped closure element orrotary ball member 50 is disposed between the body section 42 and thetail section 44. The rotary ball member 50 includes a port or fluidpassage 52 that is operable to communicate alternately with the fluidline connector portions 46 and 48 when the ball valve 34 is in a firstopened position and fluid line connector portions 46 and 47 when theball valve is in a second opened position (not shown). The fluid passage52 is sized to be substantially equal to or even slightly greater thanthe size of the fluid lines that ball valve 34 is intended to service.The rotary ball member 50 also includes a slot 54 for receiving a stemhead 56 of a ball stem 58.

Ball seals 60 are disposed within the body section 42 and tail section44 of the ball valve 34 adjacent to the rotary ball member 50. The ballseals 60 serve to provide a seat 62 against which the rotary ball member50 may be sealed. The ball seals 60 may be made from any suitablematerial, carbon-filled teflon being one example.

A primary stem operator or ball stem 58 is included in the ball valve 34and is operable to be moved between, and therefore provide the ballvalve 34 with a first opened position and a second open position. Theball stem 58 is operable to rotate the rotary ball member 50 throughapproximately ninety degrees (90°) of travel to facilitate the positionsof the ball valve 34. The ball stem 58 is rotatably supported in thebody section 42 at a neck portion 64 by a bearing member 66. A firststem head 56, located at one end of the ball stem 58, engages a slot 54in the rotary ball member 50 for rotating the ball member 50 as the ballstem 58 is likewise rotated, as will be further described herein. Theopposite end of the ball stem 58 includes a second stem head 68 whichengages a pinion stem 70 in a similar manner as has already beendescribed with respect to the ball stem 58 and rotary ball member 50connection.

O-ring seals, generally indicated at 72, are located between the neckportion 64 and the ball stem 58 and serve to provide a fluid-tight sealbetween the neck portion 64 (and therefore the body section) 42 and theball stem 58, while still allowing the ball stem 58 to be freelyrotatably supported therein. The preferred sealing arrangement raisesthe ball valve 34 to a zero-leakage system. However, less stringentalternative sealing arrangements may be used with the ball valve 34, ifdesired.

The actuation means 36 of a first embodiment of the actuated ball valve10 of the present invention is represented in FIGS. 3 and 4. Theactuation means 36 is shown to generally include a block manifold 74 andtwo exhaust port operators 76, 78. A simplified representation of across section of the actuation means 36 is shown in FIG. 3.

The block manifold 74 includes an inlet port 80 that connects theactuation means 36 with the fluid line 30 originating on the high sideof the fluid circuit 12 in which the actuated ball valve 10 isinstalled, as shown in FIG. 2 and previously described. The inlet port80 provides a constant source of pressurized refrigerant from the highside 28 of the fluid circuit 12 to the block manifold 74. A series offluid channels 82 run within the block manifold 74 to facilitate theflow of pressurized refrigerant through the actuation means 36, as willbe further described. In addition, disposed within a chamber in theblock manifold 74, generally indicated at 84, is a rack 86 and pinion 88arrangement which serves to convert the power of the pressurizedrefrigerant into a mechanical force (i.e. a torque) that is necessary todrive the stem operator 58 on the ball valve 34, and hence the rotaryball member 50, between the ball valve's 34 opened and closed positions.

While in the preferred embodiment the block manifold 74 is manufacturedin a machining operation from aluminum, it is contemplated that othersuitable precision valve construction materials such as steel, moldedplastic, or the like could also be utilized.

With particular reference to FIGS. 3 and 4, the rack 88 is operable tobe linearly displaceable within the chamber 84 of the block manifold 74in a lateral direction as viewed in FIGS. 3 and 4. Located on oppositeends of the rack 86 are piston members 90, 92. Piston members 90, 92 aredisposed in fluid reservoirs 94, 96 on opposite ends of the blockmanifold 74. Seals 98 on each piston member 90, 92 prohibit the transferof refrigerant from the reservoirs 94, 96 into the chamber 84 in whichthe rack 86 and pinion 88 arrangement is located.

FIG. 4 shows a fragmented plan view of the rack 86 and pinion 88arrangement. As depicted, linear displacement of the rack 86 in thedirection of arrow 100, results in a corresponding angular displacementof pinion 88 in the direction of arrow 102. It should be appreciatedthat the precise dimensions for the rack 86 and pinion 88 components(e.g., length, diameter, gear pitch, etc.) are a function of thenecessary rotation for the rotary ball member 50 and any dimensionalconstraints that may be imposed upon the actuated ball valve 10.

Although a rack 86 and pinion 88 arrangement is the preferredembodiment, other means to convert the power of the pressurizedrefrigerant into an angular rotation of the rotary ball member 50 of theball valve 34 could also be utilized. For example, a rotary vane-typeactuator could be employed with the actuation means of the presentinvention.

A pinion stem 70 fixed to the pinion 88, extends downward from thepinion 88 and through the block manifold 74 into engagement with thestem operator 58 of the ball valve 34 as previously described. As such,rotation of the pinion 88 and pinion stem 70, in turn, acts to rotatethe stem operator 58 of the ball valve 34. Bearing means 104 for thepinion stem 70 can be provided at the base of the block manifold 74. Asuitable material for the construction of the rack 86 and pinion 88 iscase hardened, carbon steel, or the like.

Mounted by any suitable method on top of the block manifold on oppositesides are two exhaust port operators 76, 78. The exhaust port operators76, 78 each include an outlet port 106, 108 that is in fluidcommunication with the 25 low side 26 of the fluid circuit 12, as shownin FIG. 2. In addition, each exhaust port operator 76, 78 includes aninlet port 110, 112 and an outlet port 114, 116 that are in fluidcommunication with the fluid channels 82 of the block manifold 74,substantially as represented in FIG. 3. A solenoid 118 in each exhaustport operator functions 76, 78 as a valve to control the channeling ofrefrigerant into and out of the exhaust port operator 76, 78 accordingto command signals given by the control means 24. However, unlike priorart solenoid actuated valves 200, the solenoids 118 in the actuationmeans 36 of the present invention do not require a substantial draw ofelectrical current to operate because the size of the fluid line thateach is servicing is very small, e.g. on the order of one-quarter inch(1/4"). In fact, these solenoids 118 require a current on the order of6-10 milli-amps to operate. This, in turn, enables the actuation means36 of the present invention to communicate (electronically) directlywith the control means 24, a significant cost and efficiency advantageover prior art actuated valves.

Operation of the actuated ball valve 10 can be understood withparticular reference to FIGS. 2 and 3, where the flow of refrigerantfrom the fluid circuit 12 is indicated by arrows 120. As depicted inFIG. 3, the ball valve 34 is shown in an opened position. The followingdescribes operation of the actuated ball valve 10 upon command by thecontrol means 24 to open the ball valve 34 and establish fluidcommunication between fluid line connector portions 46 and 48 byrotating the rotary ball member 50 in a clockwise direction as indicatedby arrow 122.

Control means 24 provides the solenoid 118 of exhaust port operator 76with a milli-amp signal that is sufficient to energize the solenoid 118,thereby causing the outlet port 106 to be closed and allowing thepressurized refrigerant to pass into the reservoir 94 in the blockmanifold 74. However, the solenoid 118 of solenoid 118 exhaust portoperator 78 is not energized, thereby preventing pressurized refrigerantfrom entering reservoir 96 while simultaneously opening the outlet port108 and enabling refrigerant to vent from the reservoir 96. The force ofthe pressurized refrigerant acting on the piston member 90 causes therack 86 to be displaced in the direction as indicated by arrow 100 (FIG.4). As best seen in FIG. 4, linear displacement of the rack 86 drives acorresponding angular displacement or rotation of the pinion 88.Finally, as already described, rotation of the pinion 88 results in acorresponding rotation of the rotary ball member 50 in the ball valve34. Rotation of the ball valve 34 in the reverse direction is easilyinferred from the above description.

It should be appreciated that in the first embodiment of the presentinvention, the exhaust port operator 76, 78 solenoids 118 can bedesigned and arranged such that, in the event of a loss of power, theball valve 34 would return to a nominal position as desired (e.g.,either opened or closed) when both solenoids 118 are de-energized.Alternatively, as depicted in FIG. 3, the solenoids can be arranged suchthat, in the event of a power failure, the ball valve 34 would remain inits present state at the time of the loss of power. In addition, amanual override (not shown) can be included to cycle the ball valve 34between opened and closed positions in the event of a loss of eitherelectric or fluid power.

Furthermore, it is contemplated that the elapsed time for rotation ofthe rotary ball member 50 when the ball valve 34 is actuated (i.e. thetime required to fully cycle the ball valve 34 between an open andclosed position) can be controlled to a great degree in at least thefollowing ways. First, machined-in orifices can be located in the fluidpath of the pressurized refrigerant, such as in the fluid channels 82 inthe block manifold 74 or in those of the exhaust port operators 76, 78,to ultimately control the flow of pressurized refrigerant to the pistonmembers 90, 92, and thus the speed at which the rack 86 is displaced andthe pinion 88 rotates. Alternatively, flow control means can be placedon either or both of the exhaust ports 106,108 leaving the actuationmeans 36, resulting in the same effect. Such control, which isunavailable with the prior art solenoid-actuated valves 200,significantly assists in the prevention of the "fluid hammer" effectpreviously described.

Turning now to FIG. 5, an alternate and preferred embodiment of theactuated ball valve 10' of the present invention is depicted in asimplified drawing. Although the embodiment shown in FIG. 5 includes adifferent type of ball valve 34' than the one shown in FIG. 3, thepreference toward the second embodiment of the present invention centersaround the construction of the actuation means 36'. Consequently, thetype of ball valve 34' illustrated in FIG. 5 is not necessarily"preferred" over any other type of ball valve described herein orelsewhere.

Similar to the first embodiment of the actuated ball valve, thepreferred embodiment of the actuation means 36' of the present inventionincludes a block manifold 74' having an inlet port 80' that is inconstant fluid communication with the high side 28 of the fluid circuit12 in which the valve is located. Also similar to the previousembodiment, the actuation means 36' employs a rack 86' and pinion 88'arrangement that is disposed within the block manifold 74' for theconversion of the refrigerant power and ultimate operation of the ballvalve's stem operator.

Two exhaust port operators 76', 78' are mounted by a suitable method toopposite sides on top of the block manifold 74'. The exhaust portoperators 76', 78' each include an outlet port 106', 108' that is influid communication with the low side 26 of the fluid circuit 12 andadditional fluid ports 83', 134', 136' and 138' that are incommunication with fluid ports 82' in the block manifold 74',substantially as depicted in FIG. 5. A first exhaust port operator 78'includes a solenoid operated valve 118', generally similar to thatpreviously disclosed. However, a second exhaust port operator 76'comprises a pilot valve or reversing valve 130'.

The reversing valve 130' is shown as a balanced, multi-ported spoolvalve. As is well-known, equal fluid pressures acting on opposite sidesof the spool 132' will cause the valve to return to a predetermined or"balanced" position. However, in FIG. 5, the reversing valve 130' isshown in its "out-of-balance" position.

Operation of the preferred actuation means 36' of the present inventionto cycle the ball valve 34' to the closed position, as shown in FIG. 5,in response to a command by the control means 24' is described asfollows, with the flow of refrigerant being indicated by arrows 120'.

Control means 24' de-energizes the exhaust port solenoid 118' therebyprohibiting pressurized refrigerant from traveling to the reservoir 96'and to a first port 134' in the reversing valve 130'. Simultaneously,exhaust port outlet 108' is opened and refrigerant from the reservoir96' and the first fluid port 134' is vented to the low side 26 of thefluid circuit 12. Constant pressurized refrigerant entering a secondport 136' in the reversing valve 130', in combination with theevacuation of refrigerant from the first port 134' in the reversingvalve 130', act to move the spool 132' of the reversing valve 130' toits "out-of-balance" position. Air is allowed to enter from theatmosphere, as indicated by arrow 121', through vent 123' to prevent avacuum lock on the spool. As this occurs, pressurized refrigerantbecomes free to flow into the reservoir 94' through port 138'. From thispoint, operation of the actuation means 36' is identical to thatpreviously described with respect to actuation means 36.

To reverse the cycle of the ball valve 34' just described, control means24' causes the exhaust port solenoid 118' to be energized, therebyallowing pressurized refrigerant to enter into the reservoir 96' and thefirst port 134' in the reversing valve 130'. With refrigerant of equalpressure entering both ends of the reversing valve 130', the reversingvalve 130' will return to its balanced position. As this occurs, thespool 132' is displaced in the direction of arrow 140', causing thereservoir 94' to vent to the low side 26 of the fluid circuit 12 throughthe outlet port 106' and also closing the second port 136' to thereversing valve 130'. The resulting pressure differential between thereservoir 96' and the reservoir 94', ultimately causes rotation of theball valve 34' as described above.

The actuated ball valve of the present invention can be used with therefrigerants commonly employed in the refrigeration and air conditioningindustry, such as R-22, R-502, HP-62 and AZ-50 refrigerants.Furthermore, the present invention is not limited by the physical stateof the refrigerant; that is, it does not matter to the operation of thepresent invention if the refrigerant is in a liquid, vapor or gaseousstate. However, it is contemplated that, depending upon the size of theball valve, the preferred operating pressure of the refrigerant isgenerally greater than 50 psig.

The actuated ball valve of the present invention may be manufactured toaccommodate various standard fluid line sizes and yet still incorporatemany standard components. In addition, the actuated ball valve can bereadily produced with a variety of standard "footprints", such as atwo-bolt flange surface found on typical compressor valves or any of theother fluid line connections commonly utilized, which facilitates theability to retro-fit the present valve invention into existing fluidcircuits. Further, standard sizes can be incorporated among theactuation means and the connection bracket to further enable theinterchangability of the various components of the actuated ball valve.

The actuated ball valve of the present invention, unlike the prior artactuated valves discussed above, does not inherently inhibit or obstructflow of fluid through the valve. Consequently, flow turbulence is notgenerated and therefore no corresponding pressure drop and energy lossthat results from such turbulence is present. Further, the ability toremotely actuate the ball valve provides opportunities for improving theenergy efficiency of entire refrigeration or air conditioning systems,which is expected to provide a significant economic impact upon therefrigeration and air conditioning industry.

It should be understood that while the present invention has been mainlydiscussed in the context of refrigeration and air conditioning systems,those of ordinary skill in the art will readily appreciate that theactuated valve 10 of the present invention may be utilized in any typeof fluid circuit containing an operating fluid under pressure, such asany of a variety of commonly used fluids including air, water and steam,among others.

The present invention has been described in an illustrative manner. Itis to be understood that the terminology which has been used is intendedto be in the nature of words of description rather than of limitation.Many modifications or variations to the present invention are possiblein light of the above teachings. Therefore, within the scope of theappended claims, the present invention may be practiced otherwise thanas specifically described.

What is claimed is:
 1. An actuated ball valve for use in a fluid circuitof a refrigeration or air conditioning system containing an operatingfluid under pressure and having a high-pressure side and a low-pressureside, said actuated ball valve comprising:a ball valve comprising atleast one fluid passage therethrough in combination with a valveactuation means, said combination disposed within said fluid circuitsuch that said fluid passage is in fluid communication with said fluidcircuit, said valve actuation means comprising:a manifold having aninlet port in constant fluid communication with said high-pressure sideof said fluid circuit for supplying pressurized fluid from said fluidcircuit to said valve actuation means; at least one exhaust portoperator comprising an outlet port in fluid communication with saidlow-pressure side of said fluid circuit and means for directing saidpressurized fluid to said outlet port or said manifold; a reciprocalmember disposed within said manifold for reciprocal displacementtherein; and a pinion member cooperating with said reciprocal membersuch that a displacement of said reciprocal member causes acorresponding angular displacement of said pinion member, said pinionmember also cooperating with a stem operator of said ball valve.
 2. Anactuated ball valve as set forth in claim 1 wherein each said exhaustport operator comprises a solenoid-actuated valve.
 3. An actuated ballvalve as set forth in claim 1 wherein said reciprocal member comprises arack gear having a piston member disposed on at least one longitudinalend thereof.
 4. An actuated ball valve as set forth in claim 1 furthercomprising control means for remotely cycling said actuated ball valvebetween a first position and a second position.
 5. An actuated ballvalve as set forth in claim 4 wherein said control means comprises amicroprocessor.
 6. An actuated ball valve as set forth in claim 4wherein said control means comprises an electronic switch.
 7. A fluidcircuit for use in a refrigeration or air conditioning system, saidfluid circuit comprising:a compressor; a high-pressure side located on adischarge side of said compressor; a low-pressure side located on aninput side of said compressor; an actuated ball valve, said actuatedball valve comprising a ball valve and a valve actuation means; saidball valve comprising at least one fluid passage in fluid communicationwith said fluid circuit; and said valve actuation means comprising aninlet port in constant fluid communication with said high-pressure sideof said fluid circuit and at least one outlet port in fluidcommunication with said low-pressure side of said fluid circuit.
 8. Anactuated ball valve as set forth in claim 7 further comprising controlmeans for remotely cycling said actuated ball valve between a firstposition and a second position.
 9. An actuated ball valve as set forthin claim 8 wherein said control means comprises a microprocessor.
 10. Anactuated ball valve as set forth in claim 8 wherein said control meanscomprises an electronic switch.